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EP1361365A2 - Pompe à vide et rotor en matière plastique - Google Patents

Pompe à vide et rotor en matière plastique Download PDF

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Publication number
EP1361365A2
EP1361365A2 EP03016590A EP03016590A EP1361365A2 EP 1361365 A2 EP1361365 A2 EP 1361365A2 EP 03016590 A EP03016590 A EP 03016590A EP 03016590 A EP03016590 A EP 03016590A EP 1361365 A2 EP1361365 A2 EP 1361365A2
Authority
EP
European Patent Office
Prior art keywords
rotor
vacuum pump
pump according
drive
drive element
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP03016590A
Other languages
German (de)
English (en)
Other versions
EP1361365A3 (fr
EP1361365B1 (fr
Inventor
Dieter Otto
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Magna Powertrain Hueckeswagen GmbH
Original Assignee
LuK Automobiltechnik GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=8067373&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1361365(A2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Priority claimed from DE29823809U external-priority patent/DE29823809U1/de
Application filed by LuK Automobiltechnik GmbH and Co KG filed Critical LuK Automobiltechnik GmbH and Co KG
Publication of EP1361365A2 publication Critical patent/EP1361365A2/fr
Publication of EP1361365A3 publication Critical patent/EP1361365A3/fr
Application granted granted Critical
Publication of EP1361365B1 publication Critical patent/EP1361365B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3441—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C18/3442—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the inlet and outlet opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0071—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B2200/00—Constructional details of connections not covered for in other groups of this subclass
    • F16B2200/50—Flanged connections
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T403/00—Joints and connections
    • Y10T403/70—Interfitted members
    • Y10T403/7001—Crossed rods
    • Y10T403/7003—One rod is encompassed by the other

Definitions

  • the invention relates to a vacuum pump, in particular for brake booster systems in motor vehicles, according to the preamble of Claim 1.
  • Vacuum pumps of the type mentioned here are known. You point a rotor made of metal, usually made of sintered metal, which can be set in rotation by a drive shaft. The one in one The rotor is in engagement with a wing that engages slides along a contour ring.
  • the rotor consists of several Individual parts that are releasably connected to each other. It has shown, that the rotor has a large moment of inertia due to its weight has, whereby the power consumption of the vacuum pump is undesirably high.
  • the rotor also has a massive and complex construction.
  • a vacuum pump which has the features mentioned in claim 1.
  • This draws is characterized in that the rotor is made of plastic and in one piece is trained.
  • the rotor is simpler and cheaper Can be produced in a manner, for example by injection molding, and has lighter in comparison to the known rotors. Due to the one-piece design of the rotor is a compact Construction possible, so that the space for the vacuum pump is reduced can be.
  • the power consumption of the vacuum pump is due to the small moment of inertia of the rotor relative low.
  • An embodiment of the vacuum pump is preferred, at which the rotor has at least one cavity open to the edge.
  • the cavity or cavities in simpler Way by inserting appropriately trained cores in the Injection molding tool are manufactured.
  • Cavities in the rotor can be thin walls, for example outwards and to a slot in which the wing can be moved is to be realized. Furthermore, the weight of the already light, because plastic rotors are further reduced.
  • An embodiment of the vacuum pump is also preferred, which is characterized in that the wall thickness profile of the rotor is steady or essentially steady. That is, the transition between two wall areas of different thickness is even and shows no significant changes in wall thickness on.
  • An embodiment of the vacuum pump is also preferred, at which the rotor has at least two cavities arranged side by side which are separated from each other by a rib.
  • the stiffness of the rotor is further increased by the ribbing.
  • the rib formed between two cavities is preferred thinner than the other walls of the rotor. This will Sink marks in the transition area of the rib and a wall of the rotor avoided.
  • the thickness of the rib or the In a preferred embodiment, ribs are in the range from 1.0 mm to 2.0 mm, while the wall thicknesses of the rotor in comparison, then preferably in the range from 1.5 mm to 3.0 mm lie.
  • An embodiment of the vacuum pump is also particularly preferred, which is characterized in that the rotor at least one transverse or substantially transverse to the longitudinal central axis of the rotor has running closed wall. This can ensure be that with a voided rotor no air from the drive side through the rotor into the vacuum pump can reach. So there are no additional seals necessary.
  • the vacuum pump is provided that the rotor cooperates with a drive shaft has elastic drive element.
  • a clutch or directly with the rotor Intervention is that of, for example, the internal combustion engine of a motor vehicle coupled drive shaft transmitted Torque peaks or vibrations, like them for example with direct injection engines, damped, so that breakage of the rotor is avoided with a high degree of certainty.
  • Sheet preferably spring sheet, existing drive element as Torsion bar formed, which is under the initiated torque twisted.
  • Torsion bar existing drive element as Torsion bar formed, which is under the initiated torque twisted.
  • an embodiment of the vacuum pump preferred which is characterized in that the drive element protrudes into a slot in the drive shaft and is displaceable in this is led.
  • This can advantageously be a Axial misalignment between the vacuum pump and the drive shaft can be compensated without the need for a clutch.
  • a compensation of an axis offset perpendicular to the slot can be a fixed connection of the drive element with the rotor a bending of the drive element in the elastic range compensated become. If the drive element is loosely connected to the rotor, so that it can perform a relative movement with respect to the rotor can, an axis offset is perpendicular to the slot by tilting of the drive element balanced.
  • the rotor drivable with the help of the internal combustion engine of a motor vehicle is.
  • the vacuum pump is the rotor can be driven by a motor, in particular an electric motor, even if the vacuum pump is used in a motor vehicle is, for example in connection with a brake booster system of the motor vehicle.
  • the engine can, for example also be operated hydraulically or pneumatically.
  • the rotor is optionally a variant of the internal combustion engine or driven by the engine.
  • Figure 1 shows three images of a first embodiment of the rotor 1 of a vacuum pump, not shown, with a continuous slot 3 is provided.
  • the slot 3 is used for receiving of a wing, not shown, within the slot 3 is displaceable in the diameter direction.
  • the slot 3 is in this Embodiment of the facing away from the drive of the rotor 1 End face 5 introduced into an end face 6, so it is open to the edge educated.
  • one with a torque serves as the drive Actuatable drive shaft.
  • the outer surface of the rotor 1 is cylindrical.
  • a first longitudinal section 7 of the rotor is designed as a double flat 9, on which a transmitted from the drive shaft, not shown Torque is applied to the rotor 1.
  • first Longitudinal section 7 is followed by a second longitudinal section 11 which has a larger outer diameter than the first longitudinal section 7.
  • the second longitudinal section 11 serves as a bearing 13 of the here cantilevered rotor 1.
  • the preferred type of bearing is one Plain bearing provided.
  • a larger diameter is connected to the bearing 13 third longitudinal section 15, in the radial direction seen - is broken by the slot 3 for the wing.
  • Figure 2 shows a side view and a front view of the drive side Face 17 of another embodiment of the Rotors 1, the has two bearings. Even when the rotor is supported on both sides a plain bearing is preferred.
  • the second longitudinal section 11 of the Rotor 1 forms the first bearing 13 and one on the third Longitudinal section 15 forms the fourth longitudinal section 19 the second bearing 21.
  • Both bearings 13, 21 have diameters, which are only slightly, preferably 1 mm to 5 mm, smaller than the diameter of the rotor in the area of the slot 3 for the wing, which is introduced in the third longitudinal section 15.
  • the outside diameter the bearings 13 and 21 are different here can also be identical in another embodiment.
  • the two-sided mounting of the rotor 1 has opposite to the one-sided Storage both functional advantages and advantages in the Manufacturing on.
  • the functional advantages are that the rotor not jammed in the bearing or the bearings, as is the case with a one-sided rotor sometimes occurs.
  • a compact design of the rotor is feasible because both bearings can be performed very briefly.
  • a bearing on both sides High dimensional stability. Because of the high Dimensional stability of the rotor can be tight when manufacturing the rotor Tolerances are observed.
  • Figure 3 shows two images of another embodiment of the rotor 3, which differs from that described with reference to FIG Rotor only differs in that for weight reduction Cavities are provided in the rotor.
  • On the one facing the drive End face 17 of the rotor 1 are in the end face 24 of the Bearing 13 and on the end 5 facing away from the drive in the Face 6 each introduced two cavities 23, one have circular section cross-section, as from the right Figure 3 can be seen.
  • the cavities 23 extend into the central region of the rotor or the third longitudinal section 15 extend.
  • the one between the opposing cavities The wall area that remains has only a small thickness on.
  • walls are formed by the cavities for Example the outer wall of the rotor in the area of bearings 13 and 21, which have only a small thickness. Even the walls between the slot 3 for the wing and the cavities are relative thin.
  • the shape of the cavities is variable and can also be circular or be oval. It is important that by introducing the cavities thin walls are created so that the weight of the rotor is reduced.
  • the transition between two walls, which have a different thickness is preferably stepless.
  • Figure 4 shows a side view and a plan view of the drive side End face 17 of a further exemplary embodiment of the rotor, in the case only on the end facing away from the drive 5 cavities 23 are introduced.
  • the end face 6 is one circular recess 25 introduced, which is in its middle Range extends directly to the slot 3.
  • the Recess 25 are provided with cavities 23 in the form of circular sections, which extend into the second longitudinal section 11, i.e. through the entire rotor to the first bearing 13, extend. All embodiments is common that if only from one end from cavities are introduced into this, the drive side facing end face 5 of the rotor is preferred.
  • the bearing 13 arranged on the drive side has a diameter on, which is significantly smaller than the diameter of the rotor 1 in Area of the slot 3, ie in the third longitudinal section 15. It has it has been shown that the small outside diameter of the bearing 13 a small centering diameter of the vacuum pump can be realized is.
  • the second bearing 21 facing away from the drive side is here in the Diameter only slightly smaller than the rotor 1 in the area of Wing 3.
  • the cavities 23 and the recess 25 are also here introduced into the rotor 1 from the end face 5.
  • Figure 6 shows two images of another embodiment of the rotor, in which the diameter of the second bearing 21 and that of the third longitudinal section 15, in which the slot 3 for the wing is introduced, is identical.
  • the advantage here is that on the end face 5, recess 25 made in the end face 6 and the adjoining cavities 23 are extremely thin and technically optimal wall thickness in Outside of the rotor is possible. This is with you Plastic existing rotor preferably in a range of 1.5 mm to 3.0 mm.
  • both Bearings 13, 21 the same diameter as the rotor 1 in the wing slot area exhibit.
  • Only the first, bearings 13 arranged on the drive side have the same diameter as the rotor in the region of the third longitudinal section having the slot 3 15, while the second bearing 21 has a smaller one Has diameter.
  • a rotor 1 shown in FIG. 7 has the second bearing 21, the one facing away from the drive End face 5 of the rotor 1 is provided, has a diameter, which is much smaller than the diameter of the rotor 1 in the area its third longitudinal section 15.
  • Cavities 23 introduced, as shown in the right figure of the FIG. 7 shows a cross section in the form of a circular section. Because of this configuration, in the area between the rotor outer diameter in the region of the third longitudinal section 15 and in the area of the second bearing 21 thin walls will be realized.
  • FIG. 8A shows a front view of those facing away from the drive Front side 5 of an embodiment of the rotor 1, from the several cavities are introduced.
  • the rotor 1 is symmetrical to a transverse axis 27, which is perpendicular to the longitudinal central axis 29 of the rotor 1 runs. It is therefore in the following only the cavities described above the transverse axis 27.
  • the total of three cavities 23A, 23B and 23C are small Distance arranged side by side.
  • the cavity 23B is separated from the cavities 23A and 23C by a rib 31, that of a wall of the one-piece rotor 1 is formed.
  • the ribs 31 increase the stiffness of the rotor 1 and are preferably thinner than the other walls of the Rotors, around sink marks, i.e.
  • the cavities 23A to 23C have a circular section shape, whereby due to the V-shaped arrangement of the ribs 31 of the central cavity 23B has a circular cross-section.
  • the cavities are thin walls, especially in the outer areas of the rotor.
  • the embodiment of the rotor 1 shown in FIG. 8B differs only differ from that described with reference to FIG. 8A in that the ribs 31 here at a distance and parallel are arranged to each other. It is clear that the arrangement the ribs can be varied and preferably depending on the required Stiffness properties is set.
  • FIG. 9 shows a side view of a further exemplary embodiment of the rotor 1, from the end faces 17 and 5 of which there are cavities 23 or a recess 25 and subsequent Cavities 23 are introduced into the bearings 13 and 21.
  • the cavities 23 extend into the central area of the rotor.
  • the rotor 1 has an imaginary, essentially transverse to it Longitudinal central axis 29 running closed wall 33, the Course is shown with a dashed line.
  • the wall 33 extends viewed across the entire length of the rotor Rotor cross section and includes here first bearing 13 facing the drive side. This ensures that despite the cavities 23 from the drive side, no air through the rotor 1 can get into the vacuum pump.
  • the clutch 35 shown in FIG. 10A is from a disk 37 formed in the central region of a rectangular slot 39 is introduced that penetrates the disc 37.
  • the elongated hole 39, in the drive shaft with a correspondingly trained section engages enables compensation of an axis offset between the vacuum pump and the drive shaft.
  • the disc is preferably designed such that they are produced by stamping can be.
  • the circular cross-section Disk 37 has two on opposite sides in the circumference recesses introduced, creating a contact surface 41 is formed, which is preferably as shown in FIG. 10A is.
  • each bearing surface 41 is on one on the rotor 1 provided counter surface 43 can be pressed.
  • the shape of the recess is chosen so that despite small Diameter d of the disc 37 between the contact surfaces the rotor 1 and the clutch are large. Because of the large contact areas the surface pressure in these areas is small, so that the clutch hardens if it is made of steel or sintered iron exists, can optionally be dispensed with.
  • the ratio between the thickness b and the diameter d of the disk 37 in a range of 0.1 ⁇ b / d ⁇ 0.3.
  • the counter surfaces 43 are in one piece with each the drive segment connected to the rotor 45A or 45B, which protrude like a dome over the end face 24 of the first bearing 13.
  • the distance between the drive segments 45A, 45B and their shape is chosen so that the coupling with play between the drive segments and arranged in a small Angular range is pivotable about its central longitudinal axis.
  • the rotor 1 has a very stable shape in its drive area. This is This has become possible in particular because it is a very large one Support length I of the drive segments 45A and 45 B in the direction of the force is realized. So is preferably a ratio between the support length I and the diameter D of the rotor 1 realized in one Section 0.35 ⁇ I / D ⁇ 0.65.
  • the drive segments 45A, 45B by a closed Ring 47 connected together, which gives the stiffness of the rotor 1 can be increased.
  • the ring 47 can also be used as a bearing, especially for plain bearings, for the rotor. This Embodiment of the rotor is very compact in the axial direction.
  • the clutch 35 is in the middle area instead of one Elongated a double 49 is provided, which in a corresponding trained slot engages in the drive shaft. Over the double 49 the torque from the drive shaft to the clutch transfer.
  • FIG. 10C shows a top view of the end face 17 of the embodiment shown in FIG Figure 10A described rotor 1 in a further embodiment a clutch 35, which is formed by a disk 37 '. Same Parts are provided with the same reference numerals so that their Description is made to Figure 10A.
  • Disk 37 ' two identical recesses are made, whereby each have a flat bearing surface 41 and one at right angles thereto or substantially perpendicular to the support surface 41 Sidewall 46 is formed.
  • FIG. 11 shows what has been described with reference to the previous figures Embodiment of the rotor 1, the first, as a double 9 formed longitudinal section 7.
  • the cone-shaped Double 9 is with a cup-shaped, preferably made of sheet metal Provide cap 51, which is pressed onto the double or can be clipped on. It is also possible that the cap is already inserted into the mold when the rotor is sprayed and thus inextricably linked to the rotor during manufacture becomes.
  • the cap 51 protects the double 9, the strength of the Transfer the required torque is sufficient before one Wear caused by a relative movement between the double and a clutch or with a direct drive of the rotor, that is, without a clutch, between the double and the drive shaft is caused.
  • Figure 12 shows a greatly enlarged section of the first Longitudinal section 7 applied cap 51, the at least one Has pressure point 53, whereby on the inside of the cap 51st a protrusion is formed which in a in the flat of the rotor 7th introduced recess 55 engages positively.
  • This can the elastic and / or consisting of an elastic material Cap 51 can be clipped onto the double 9 in a simple manner.
  • Figure 13 shows a longitudinal section and a plan view of the drive side Face 17 of another embodiment of a Rotor 1, which is formed in one piece and consists of plastic.
  • the rotor 1 here comprises a drive shaft, not shown cooperating elastic drive element 57, for example made of sheet metal, preferably spring sheet.
  • the Legs 59 and 59 'of the U-shaped drive element 57 are in one recess 61 each is made in the rotor 1.
  • the end areas of the two legs are cast in the rotor 1, whereby the drive element 57 is permanently connected to the rotor 1.
  • the Recesses 61 extend from the end face 24 of the first Bearing 13 to beyond the central region of the rotor, wherein the size of the recesses is chosen so that the legs 59, 59 'in the area of the recesses relative to the rotor can move.
  • the section connecting the legs 59, 59 ' 63 of the one-piece drive element 57 projects over the end face 24 out.
  • the arrangement of the recesses 61 is chosen so that the legs 59, 59 'a large area of the slot 3 in which enclose the wing of the vacuum pump. by virtue of With this configuration, the drive torque is here directly in the areas initiated the rotor, on which the slidable in the slot 3 supported wing of the vacuum pump.
  • the drive element engages 57 with its section 63 in a slot in the drive shaft on.
  • the drive shaft rotates, the drive torque introduced into the rotor via the drive element 57, the elastic Drive element 57 occurring torque peaks smoothes.
  • the Legs 59, 59 'each have two pressure points 67 in their end regions on, causing a convex on one side of the drive element and a concave curvature is formed on the other side.
  • the convex curvatures in the ends of the legs serve to hold the two legs 59, 59 'in the recesses 61 to jam so that the drive element 57 securely on or is held in the rotor.
  • the for inserting the legs contact pressure required in the recesses is relatively low.
  • the portion engaging in a slot of the drive shaft 63 of the drive element 57 can also be arranged without play in this slot section 63 points on each side of the drive element each have two pressure points 67, in the area of which the drive element has a concave or convex curvature. Due to the pressure points 67 on both sides, at one oscillating movement of the drive element 57, for example in Sequence of torque vibrations, a back and forth beating Leg in the recesses and section 63 in the Slot of the drive shaft prevented because the drive element 57 in these areas with both sides in the recesses respectively fits the slot.
  • FIG. 15 shows a side view of a further exemplary embodiment an elongated drive element 57, the opposite at its ends Pages each has two pressure points 67, whereby concave and convex curved areas are formed.
  • elastic Drive elements 57 can - as can be seen from FIG Axial misalignment a between the vacuum pump and the drive shaft can be compensated for without the need for a clutch.
  • the drive element 57 projects into this a slot 69 of a drive shaft 71.
  • the other end of the drive element 57 protrudes into a slot or into a recess in the Rotor 1.
  • the Drive element 57 can this instead of the pressure points 67 in his end as shown in FIG. 17 also have spherical surface sections 73, the on both sides of the drive element 57 by one Material order are formed or with the drive element 57 are connected in one piece. This ensures that the drive torque not over the edges of the thin drive element 57 is transmitted, but over areas.
  • Figure 18 shows a section of a rotor 1 in the region of a recess 61 for the legs 59, 59 'of the U-shaped drive element, in the reason a receptacle 75 for clamping the End regions of the legs are provided.
  • a top view of the recesses 61 in the rotor shows, is a receptacle for each leg of the drive element 57 75 are provided, each of which is formed by a web 77, the has a slot into which one leg of the drive element is pressed.
  • FIG. 20 shows one with play in a recess 61 in the rotor 1 inserted drive element 57, which is offset by an axis Can compensate for tilting.
  • the drive element 57 is in his Investment area spherical on both sides, that is, the The drive element has one on both sides of its end region convex curvature.
  • Particularly advantageous in the case of FIG. 20 illustrated embodiment is that by tilting the Drive elements in the event of an axis offset, however, no additional Bearing force arises, but that only the torque in the rotor is initiated.
  • the spherical end regions of the drive element 57 prevent the torque not over edges, but over spherical surfaces is transmitted.
  • the recesses 61 receiving the drive element 57 in the Rotor 1 are preferably designed so that the deforming under load Drive element 57 in the rotor at a stop to the system comes before the area of plastic deformation is reached. This is the case in the embodiment shown in FIG of the rotor 1 several stop surfaces 77 are provided, which on both Sides of the drive element 57 are arranged.
  • FIG. 22 shows an end region of an exemplary embodiment of the drive element 57, which is angled twice here, which makes it in advantageously to different sized slots in the drive shaft and can be adapted to the rotor.
  • Figure 23 shows three images of another embodiment of the rotor 1, the one described with reference to the previous figures Drive element 57 and several, from both ends 5 and 17 introduced cavities 23, which reduce weight serve the rotor.
  • the walls of the rotor 1 have plastic-appropriate Strengths on.
  • the legs 59, 59 'of the drive element 57 are so long here that they completely slot 3 for the wing surrounded and reach to the second camp 21.
  • the thigh ends are completely surrounded by the rotor material and therefore cannot be removed connected to the rotor. Because of this configuration, the drive torque directly into the end facing away from the drive of the rotor, so that the remaining areas of the rotor 1 are at least essentially stress-free.
  • the plastic rotor shows opposite Existing rotors have a low weight due to metal the introduction of at least one cavity is further reduced becomes.
  • the cavities can be made in an injection molding process Rotor formed by inserting cores into the mold or after the rotor is machined from it be worked out. The shape, design and number the cavities can be varied and is determined, for example, by the the rotor can be applied drive torque.
  • each voided embodiment of the rotor with stiffening ribs 31 can be provided, as shown in FIGS. 8A and 8B.
  • the vacuum pump can also be arranged in areas, in which there are high temperatures, for example in the engine compartment a motor vehicle, the rotor in a preferred embodiment made of a plastic whose fatigue strength preferably at least up to 80 ° C can be guaranteed.
  • a plastic whose fatigue strength preferably at least up to 80 ° C can be guaranteed.
  • such plastics can also be used which at least up to 140 ° C and above their strength properties, at least essentially, don't lose.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
EP03016590A 1998-09-30 1999-09-24 Pompe à vide et rotor en matière plastique Expired - Lifetime EP1361365B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE29823809U DE29823809U1 (de) 1998-09-30 1998-09-30 Vakuumpumpe
DE29823809U 1998-09-30
EP99947419.0A EP1117933B2 (fr) 1998-09-30 1999-09-24 Pompe a vide

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP99947419.0A Division EP1117933B2 (fr) 1998-09-30 1999-09-24 Pompe a vide
EP99947419.0 Division 1999-09-24

Publications (3)

Publication Number Publication Date
EP1361365A2 true EP1361365A2 (fr) 2003-11-12
EP1361365A3 EP1361365A3 (fr) 2003-12-03
EP1361365B1 EP1361365B1 (fr) 2005-08-10

Family

ID=8067373

Family Applications (2)

Application Number Title Priority Date Filing Date
EP99947419.0A Expired - Lifetime EP1117933B2 (fr) 1998-09-30 1999-09-24 Pompe a vide
EP03016590A Expired - Lifetime EP1361365B1 (fr) 1998-09-30 1999-09-24 Pompe à vide et rotor en matière plastique

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP99947419.0A Expired - Lifetime EP1117933B2 (fr) 1998-09-30 1999-09-24 Pompe a vide

Country Status (6)

Country Link
US (3) US6923628B1 (fr)
EP (2) EP1117933B2 (fr)
JP (1) JP2002525498A (fr)
DE (4) DE29924585U1 (fr)
GB (1) GB2359591B (fr)
WO (1) WO2000019104A1 (fr)

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DE102004034925B3 (de) * 2004-07-09 2006-02-16 Joma-Hydromechanic Gmbh Einflügelvakuumpumpe
WO2006042493A1 (fr) * 2004-10-22 2006-04-27 Luk Automobilitechnik Gmbh & Co. Kg Pompe
ITMI20101984A1 (it) * 2010-10-26 2012-04-27 O M P Officine Mazzocco Pagnoni S R L Pompa monopaletta

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EP1960649A4 (fr) * 2005-12-01 2015-06-17 David D Gray Appareil de combustion rotatif
ITTO20060263A1 (it) * 2006-04-11 2007-10-12 Vhit Spa Rotore per pompa a palette in materia plastica rinforzata da lamine metalliche
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EP2746532B1 (fr) 2012-12-19 2018-02-14 Pierburg Pump Technology GmbH Agencement de rotor pour une pompe à vide ainsi que la pompe à vide dotée d'un tel agencement de rotor
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US9739149B2 (en) * 2013-08-05 2017-08-22 Charles Tuckey Vane pump assembly
EP3032105B1 (fr) * 2014-12-12 2021-05-19 Pierburg Pump Technology GmbH Pompe à vide mécanique pour véhicule automobile
EP3034779B1 (fr) 2014-12-18 2018-02-14 Pierburg Pump Technology GmbH Pompe à vide de véhicule automobile
DE102016114959A1 (de) * 2016-08-11 2018-02-15 B. Braun Avitum Ag Peristaltikpumpe mit rotatorischem Spiel
WO2018137045A1 (fr) 2017-01-30 2018-08-02 Litens Automotive Partnership Système de pompe à vide à embrayage
CA3112348A1 (fr) 2018-09-11 2020-03-19 Rotoliptic Technologies Incorporated Machines rotatives trochoidales helicoides et trochoidales decalees
US11815094B2 (en) 2020-03-10 2023-11-14 Rotoliptic Technologies Incorporated Fixed-eccentricity helical trochoidal rotary machines
US11802558B2 (en) 2020-12-30 2023-10-31 Rotoliptic Technologies Incorporated Axial load in helical trochoidal rotary machines
CA3177204A1 (fr) 2021-01-08 2022-07-14 Rotoliptic Technologies Incorporated Machines rotatives a rotors en forme de goutte
US12146492B2 (en) 2021-01-08 2024-11-19 Rotoliptic Technologies Incorporated Helical trochoidal rotary machines with improved solids handling

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004034925B3 (de) * 2004-07-09 2006-02-16 Joma-Hydromechanic Gmbh Einflügelvakuumpumpe
WO2006042493A1 (fr) * 2004-10-22 2006-04-27 Luk Automobilitechnik Gmbh & Co. Kg Pompe
US7866967B2 (en) 2004-10-22 2011-01-11 Luk Automobiltechnik Gmbh & Co. Kg Pump having an intermediate element with a pivot bearing within a rotor for connecting the rotor with a coupling device
ITMI20101984A1 (it) * 2010-10-26 2012-04-27 O M P Officine Mazzocco Pagnoni S R L Pompa monopaletta
WO2012056295A3 (fr) * 2010-10-26 2013-06-27 O.M.P. Officine Mazzocco Pagnoni S.R.L. Pompe à aube unique

Also Published As

Publication number Publication date
US20030185696A1 (en) 2003-10-02
US20020192097A1 (en) 2002-12-19
EP1361365A3 (fr) 2003-12-03
DE19964598B4 (de) 2013-12-12
DE19981942B4 (de) 2009-07-23
EP1117933B1 (fr) 2004-04-14
GB0108756D0 (en) 2001-05-30
GB2359591B (en) 2003-04-02
DE29924585U1 (de) 2004-01-08
EP1361365B1 (fr) 2005-08-10
JP2002525498A (ja) 2002-08-13
DE29924457U1 (de) 2003-04-17
GB2359591A (en) 2001-08-29
EP1117933A1 (fr) 2001-07-25
WO2000019104A1 (fr) 2000-04-06
US6648619B2 (en) 2003-11-18
US6923628B1 (en) 2005-08-02
DE19981942D2 (de) 2001-10-18
US6743004B2 (en) 2004-06-01
EP1117933B2 (fr) 2013-04-17

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